CN201513541U - Mechanical-hydraulic interactive continuously variable transmission - Google Patents

Abstract

A mechanical-hydraulic interactive continuously variable transmission, comprising an input part, a combined hydraulic pump (31), a planetary gear transmission part (30), and an output part, which are sequentially connected, and the output part includes a hydraulic motor and an output shaft (1), The combined hydraulic pump (31) and the hydraulic motor form a hydraulic system through the hydraulic circuit, the input part drives the combined hydraulic pump (31) through the planetary gear transmission part (30), the above-mentioned combined hydraulic pump drives the hydraulic motor to rotate through the hydraulic circuit, the hydraulic motor and Both planetary gear transmission parts (30) drive the output shaft (1) to rotate at the same time, and the output shaft (1) is used as the output of the entire continuously variable transmission. With this structure, stepless continuous shifting can be realized, and gear disengagement and shifting are not required during shifting, and the speed ratio can be precisely controlled, which can be used for any mechanical equipment that needs shifting, especially for automobiles.

Description

Mechanical-hydraulic interactive continuously variable transmission

technical field

The utility model relates to the field of stepless speed change, and can also be used as a soft start device for starting with load.

Background technique

In various fields where mechanical equipment is used, most of the systems that need to transmit speed and power need speed change devices. At present, there are two kinds of speed changers: stepped speed change and stepless speed change. Although the structure of the stepped speed changer is relatively simple, the speed change is discontinuous, has jumps, is not stable, and the speed change control is more loaded down with trivial details. Continuously variable transmissions are stable and soft, and can perform continuous transmission within a certain range, but often have complex structures and high manufacturing costs. Especially in the automotive industry, continuously variable transmissions can only be equipped on some high-end and luxurious cars. rise. In addition, whether there is a step automatic transmission or a stepless automatic transmission on the current car, its transmission mode is a purely mechanical structure, and generally the size, structure and related parameters of the transmission parts must be strictly controlled according to the transmission speed ratio. match. Secondly, due to the limitation of structural principles, most of them can only be used on light cars with less transmission power.

Utility model content

The purpose of the utility model is to provide a stepless speed change device with simple structure, low manufacturing cost, stable speed change, easy control and perfect combination of gear transmission and hydraulic transmission. The utility model is mainly based on the mechanical transmission, and the hydraulic transmission plays the role of variable speed control and auxiliary transmission.

The utility model provides a mechanical-hydraulic interactive continuously variable transmission, which includes an input part, a combined hydraulic pump, a planetary gear transmission part, and an output part, which are connected in sequence. The output part includes a hydraulic motor and an output shaft, and the combined hydraulic pump It forms a hydraulic system with the hydraulic motor through the hydraulic circuit. The input part drives the combined hydraulic pump through the planetary gear transmission part. The above combined hydraulic pump drives the hydraulic motor to rotate through the hydraulic circuit. Both the hydraulic motor and the planetary gear transmission part drive the output shaft to rotate at the same time. , the output shaft is used as the output of the entire continuously variable transmission.

Preferably, the above-mentioned input part includes an input shaft with a power disc, and the above-mentioned power disc is connected to the combined hydraulic pump; the combined hydraulic pump includes a plurality of sub-pumps, and the input shafts of the sub-pumps are respectively connected to the planetary shaft gears of the respective corresponding planetary gear transmission parts. The shaft is in the same body, the output shaft of the output part is in the same body as the ring gear of the planetary gear transmission part, and the output shaft is shared with the output shaft of the hydraulic motor.

Preferably, the above-mentioned hydraulic motor is a variable-speed motor, and stepless continuous speed change is realized by controlling the displacement of the above-mentioned motor.

Preferably, the combined hydraulic pump is a combined gear pump, and the combined gear pump includes a rear end cover, a pump body, a front end cover, a sun gear and a plurality of planetary gears, the sun gear is arranged on the input shaft, and the plurality of planetary gears surround the sun The gears are arranged around and meshed with them, and the above-mentioned multiple planetary gears are respectively fixedly connected with the shafts of the planetary shaft gears.

Preferably, a plurality of oil inlet holes and a plurality of oil outlet holes are opened on the circumference of the front end cover at uniform intervals in the axial direction and sequentially intersect, and first and second annular oil grooves are also opened in the radial direction of the front end cover, The plurality of oil inlet holes respectively extend to the second annular oil groove and communicate with each other, and the plurality of oil outlet holes respectively extend to the first annular oil groove and communicate with each other.

Preferably, the above-mentioned oil inlet holes, oil outlet holes, planetary gears, and planetary shaft gears have the same number, preferably three.

Preferably, the above-mentioned hydraulic motor is a swash plate variable displacement axial piston motor, which is equipped with a swash plate angle control mechanism, the upper end of the swash plate of the swash plate variable displacement axial piston motor and the output end of the swash plate angle control mechanism Hinged fit, by controlling the angle of the swash plate, the displacement of the hydraulic motor can be controlled for stepless and continuous speed change.

Preferably, the input part further includes a housing and a distribution sleeve, the housing is provided with two radial holes, and the distribution sleeve is provided with a radial hole and a radial oblique hole; the swash plate type variable axial plunger The motor includes a distribution plate, and the distribution plate is provided with an oil inlet groove and an oil outlet groove. The second annular oil groove passes through the radial hole on the flow distribution sleeve, one of the radial holes on the casing and an oil delivery pipe, and then connects with the above flow distribution plate. The first annular oil groove communicates with the oil inlet groove on the above-mentioned valve plate after passing through the radial inclined hole on the above-mentioned distribution sleeve, another radial hole on the above-mentioned housing, and another oil delivery pipe in sequence.

Through the above description of the utility model structure, the utility model has the following main advantages:

1. Stepless continuous speed change can be realized, no gear disengagement and shifting are required during speed change, and the speed ratio can be precisely controlled.

2. The transmission speed ratio has no direct relationship with the number of gear teeth.

3. When the transmission speed ratio gradually increases from a number greater than zero (can be set) to 1, the rotation speed of all transmission gears (except the ring gear) gradually slows down. When the output speed reaches the input speed (that is, the speed ratio is 1 ), the gears will no longer rotate on their own (except the ring gear), and all gears will stop meshing, which can effectively control heat generation. Therefore, its high-speed transmission performance is excellent.

4. The structure is simple and the manufacturing cost is low. After simple comparison with the structure of the existing transmission with the same function on the automobile, its overall size and weight are not greater than one-half of the existing transmission.

5. The speed changer can be scaled up or down in proportion, and can be used in any mechanical equipment that needs speed change.

6. The transmission can also be used as a soft start device with load start.

Brief description of the drawings

Fig. 1 is a circular expansion diagram of the transmission principle of the present invention, wherein: A is a front view, and B is a schematic cutaway view along the line A-A in Fig. 1A.

Fig. 2 is a schematic diagram of the main structure of a case of the present invention.

Fig. 3 is a sectional view of a case A-A of the utility model, showing a diagram of the oil circuit of the distribution plate.

Fig. 4 is a sectional view of a case B-B of the utility model, showing the meshing state of the planetary shaft gear and the ring gear.

Fig. 5 is a C-C sectional view of a case of the utility model, showing a schematic diagram of the main structure of the combined gear pump.

Fig. 6 is a D-D sectional view of a case of the present utility model, showing the direction diagram of the oil circuit.

Fig. 7 is an E-E sectional view of a case of the present utility model, showing the direction of the oil suction circuit.

Fig. 8 is a partial sectional view of case F-F of the present utility model, showing the layout of oil and oil suction pipelines.

Symbol Description

1 - output shaft;

201, 202, 203, 204-rolling bearings;

3- swash plate seat;

4 - plunger;

5 - swash plate;

6- Swash plate angle control mechanism;

7-distribution plate;

8 - planetary gear;

9-Rear end cover of combined gear pump;

10- Combined gear pump pump body;

11-Combined gear pump front cover;

12-bolt;

13 - sun gear;

14 - housing;

151, 152-oil pipeline;

16-input shaft with power disc;

17-distribution sleeve;

18-locating pin;

191, 192-annular oil tank;

20-oil inlet tank;

2101, 2102 - rolling pin;

22 - needle bearing;

2301, 2302, 2303-coupling keys;

24 - plunger cylinder;

2501, 2502, 2503-oil inlet hole;

26-planetary shaft gear;

2701, 2702, 2703-oil outlet;

28-oil outlet tank;

29-variable hydraulic motor;

30-planetary gear transmission part;

31 - Combined hydraulic pump.

Detailed ways

The utility model is characterized in that it contains: an input part 16, an output part 1, a planetary gear transmission part 30, a combined hydraulic pump 31 and a variable hydraulic motor. The basic working principle of the utility model is that after the input shaft 16 inputs power, the output shaft 1 does not necessarily rotate or slowly rotate due to the load, and at this time, the planetary shaft gear 26 that cooperates with the ring gear rotates with the input shaft 16 , while rotating at a higher speed. From the analysis of the motion relationship of the planetary shaft gear 26 relative to the ring gear, it can be seen that when the rotational speed of the input shaft 16 driving the planetary shaft gear 26 to revolve is constant, the slower the rotation speed of the planetary shaft gear 26, the faster the rotational speed of the output shaft 1, When the rotation speed of the planetary shaft gear 26 is zero, the rotational speed of the output shaft 1 is equal to the rotational speed of the input shaft 16 , and the transmission speed ratio at this moment is 1, which is equivalent to the rigid connection between the output shaft 1 and the input shaft 16 .

In order to achieve the above-mentioned transmission effect and to transmit the motion of the input shaft 16 to the output shaft 1 accurately according to a certain speed ratio, the rotation speed of the planetary shaft gear 26 must be precisely controlled. The technical scheme adopted by the utility model is realized by controlling the rotational speed of the sub-pumps in the combined hydraulic pump 31 respectively connected with the above-mentioned planetary shaft gears 26. According to the basic principle of hydraulic transmission, it can be achieved by controlling the hydraulic pressure at the outlet of the sub-pumps. The purpose of controlling the rotation speed of the sub-pump and reaching the rotation speed of the above-mentioned planetary shaft gear 26. The outlet pressure of the sub-pump is controlled by the variable hydraulic motor 29, and the variable hydraulic motor 29 is rigidly connected to the output shaft 1, which is in turn connected to the load. Through the design of the above technical scheme, the hydraulic transmission not only plays the role of mechanical speed change control, but also plays the role of power transmission. In actual operation, the mechanical transmission and hydraulic transmission produce an interactive effect.

In order to further clarify the feasibility and effectiveness of the utility model, an implementation example of the utility model is introduced below through Fig. 2 to Fig. 8 . One of the implementation cases of the utility model is characterized in that it contains: an input part, an output part, a planetary gear transmission part, a combined gear pump and a variable axial plunger motor, wherein:

The input part includes: an input shaft 16 with a power disc, a housing 14 and a distribution sleeve 17, the input shaft 16 is in rolling fit with the housing 14 through a first rolling bearing 201, and the distribution sleeve 17 is connected to the housing through a positioning pin 18 Body 14 is fixedly connected, and at the same time, the flow distribution sleeve 17 is in clearance fit with the input shaft 16, and radial holes are opened on the above-mentioned casing 14, and radial holes and radial oblique holes are opened on the above-mentioned flow distribution sleeve 17.

The output part is a swash plate type variable displacement axial piston motor, the right end of the output shaft 1 is provided with a coaxial ring gear, the left end of the output shaft 1 is rollingly fitted with the swash plate seat 3 through the third rolling bearing 203, The right end of the output shaft 1 rolls with the distribution plate 7 through the fourth rolling bearing 204, and the distribution plate 7 is fixedly connected with the above-mentioned housing 14, and the plunger cylinder 24 is fastened coaxially with the above-mentioned output shaft 1 through the second coupling key 2302 connection, the swash plate 5 and the above-mentioned swash plate seat 3 make a spherical sliding fit, and the plungers 4 distributed on the circumference of the above-mentioned plunger cylinder 24 make an axial sliding fit with the above-mentioned plunger cylinder 24, and at the same time, the above-mentioned plunger 4 and the above-mentioned swash plate 5 It is also used for circular rotation sliding fit. The right end surface of the above-mentioned plunger cylinder 24 is slidingly fitted with the left end surface of the above-mentioned flow distribution plate 7 along the circumferential direction. The output end of the angle control mechanism 6 is hingedly fitted, and oil inlet grooves 20 and oil outlet grooves 28 are distributed symmetrically along the circumferential direction on the flow plate 7 .

The combined gear pump part includes the input shaft 16 power plate, the rear end cover 9, the pump body 10 and the front end cover 11, which are connected by bolts 12 in sequence from left to right. There are three oil inlet holes 2501, 2502, 2503 and three oil outlet holes 2701, 2702, 2703. There are also two annular oil grooves 191, 192 in the radial direction of the front end cover 11. The above three oil inlet holes 2501 , 2502, 2503 respectively extend to the above-mentioned annular oil groove 192 and then communicate with each other, the above-mentioned three oil outlet holes 2701, 2702, 2703 respectively extend to the annular oil groove 191 and then communicate with each other, and the above-mentioned annular oil groove 192 passes through the radial direction on the above-mentioned distribution sleeve 17 in turn. The hole, the radial hole on the housing 14 and the oil delivery pipe 152 communicate with the oil outlet groove 28 on the above-mentioned distribution plate 7. The oil inlet groove 20 on the above-mentioned distribution plate 7 communicates with the hole and the above-mentioned oil delivery pipe 151 .

The planetary gear transmission part includes: three planetary shaft gears 26 with the same structure, three planetary gears 8 with the same structure, and a sun gear 13, each of the above-mentioned planetary shaft gears 26 is connected to the above-mentioned input shaft through the second rolling bearing 202 16. The power plate at the left end is used for rolling fit, and it also rolls with the rear end cover 9 of the above-mentioned combined gear pump through the first rolling pin 2101, and rolls with the front end cover 11 of the above-mentioned combined gear pump through the second rolling pin 2102. Cooperate, the above-mentioned three planetary shaft gears 26 are meshed with the ring gear on the above-mentioned output shaft 1, and the three planetary shaft gears 26 are respectively respectively connected with the above-mentioned three planetary gears 8 in the pump body 10 of the above-mentioned combined gear pump. The three planetary gears 8 are in mesh with the above-mentioned sun gear 13 installed in the above-mentioned pump body 10 together by connecting keys 2301, 2302 (not shown in the figure), and 2303 (not shown in the figure) in the same manner. , the sun gear 13 is in rolling fit with the input shaft 16 coaxially through the needle bearing 22 .

The basic structure of a kind of implementation case of the utility model has been described above. The basic working principle of the above-mentioned case of the utility model is that after the input shaft 16 is powered, the output shaft 1 does not necessarily rotate or slowly rotate due to the load. The three planetary shaft gears 26 matched by the ring gear rotate with the input shaft 16 and rotate at a relatively high speed simultaneously. From the analysis of the motion relationship of the three planetary shaft gears 26 relative to the ring gear, it can be seen that when the rotational speed of the input shaft 16 driving the three planetary shaft gears 26 to revolve is constant, the slower the rotation speed of the three planetary shaft gears 26, the slower the output shaft 1 The faster the rotation speed, when the rotation speed of the three planetary shaft gears 26 is zero, the rotation speed of the output shaft 1 is equal to the rotation speed of the input shaft 16. At this time, the transmission speed ratio is 1, which is equivalent to the output shaft 1 and the input shaft 16. The shaft 16 is rigidly coupled. Then, in order to accurately transmit the motion of the input shaft 16 to the output shaft 1 according to a certain speed ratio, the rotation speeds of the three planetary shaft gears 26 must be precisely controlled. The measures taken by the utility model are realized by controlling the rotation speeds of the three planetary gears 8 in the combined gear pump which are connected respectively with the three planetary shaft gears 26 . The three planetary gears 8 in the pump body 10 together with the sun gear 13 in the pump body 10 constitute a combined gear pump element. When the three planetary shaft gears 26 force the three planetary gears to When the gear 8 rotates in the direction shown in Figure 4, the three holes 2701, 2702, 2703 form oil outlet holes, and the three holes 2501, 2502, 2503 are oil suction holes. If the rotation speed of the three planetary gears 8 is controlled by controlling the hydraulic pressure of the three oil outlet holes 2701, 2702, 2703, the purpose of controlling the rotation speed of the three planetary shaft gears 26 is also achieved. The three oil outlet holes 2701, 2702, and 2703 communicate with the oil inlet groove 20 on the oil distribution plate 7 of the swash plate variable axial piston motor through a set of pipeline passages. According to the working principle, the hydraulic pressure of the oil inlet tank 20 is related to the inclination angle of the swash plate 5, so as long as the inclination angle of the swash plate 5 is directly controlled, the purpose of stepless speed change can be realized. It should also be noted here that the hydraulic pressure of the three oil outlet holes 2701, 2702, 2703 can also be controlled by means of hydraulic throttling, and the purpose of continuously variable speed can also be achieved, but this will cause energy loss. The reason why the output shaft 1 is equipped with a swash plate variable displacement axial piston motor is to make it not only play the role of variable speed control, but also maximize the effectiveness of power transmission.

Claims (11)

1. A mechanical-hydraulic interactive continuously variable transmission, characterized in that it includes an input part, a combined hydraulic pump (31), a planetary gear transmission part (30), and an output part, which are connected in sequence, and the output part includes a hydraulic motor and The output shaft (1), the combined hydraulic pump (31) and the hydraulic motor form a hydraulic system through the hydraulic circuit, the input part drives the combined hydraulic pump (31) through the planetary gear transmission part (30), and the combined hydraulic pump drives through the hydraulic circuit The hydraulic motor rotates, and both the hydraulic motor and the planetary gear transmission part (30) simultaneously drive the output shaft (1) to rotate, and the output shaft (1) serves as the output of the entire continuously variable transmission. 2. The continuously variable transmission according to claim 1, characterized in that, the input part includes an input shaft (16) with a power disc, and the power disc is connected to a combined hydraulic pump (31); the combined hydraulic pump ( 31) It includes a plurality of sub-pumps, the input shafts of the sub-pumps are respectively in the same body as the planetary shaft gears (26) of the corresponding planetary gear transmission parts (30), and the output shaft (1) of the output part and the planetary gear transmission part (30) The ring gear is in the same body, and the output shaft (1) is shared with the output shaft of the hydraulic motor (29) simultaneously. 3. The continuously variable transmission according to claim 1 or 2, characterized in that the hydraulic motor is a variable displacement motor, and stepless continuous transmission is realized by controlling the displacement of the motor. 4. The continuously variable transmission according to claim 2, characterized in that the combined hydraulic pump (31) is a combined gear pump, and the combined gear pump includes a rear end cover (9), a pump body (10), a front end cover ( 11), a sun gear (13) and a plurality of planetary gears (8), the sun gear (13) is arranged on the input shaft (16), and the plurality of planetary gears (8) are arranged around the sun gear (13), and meshed with it, the plurality of planetary gears (8) are fixedly connected with the shafts of the planetary shaft gears (26) respectively. 5. The continuously variable transmission according to claim 4, characterized in that, a plurality of oil inlet holes (2501, 2502, 2503) are opened on the circumference of the front end cover (11) at uniform intervals in the axial direction and sequentially intersecting And a plurality of oil outlet holes (2701, 2702, 2703), first and second annular oil grooves (191, 192) are also opened in the radial direction of the front end cover (11), and the plurality of oil inlet holes (2501, 2502, 2503) respectively extend to the second annular oil groove (192) and communicate with each other, and the plurality of oil outlet holes (2701, 2702, 2703) respectively extend to the first annular oil groove (191) and communicate with each other. 6. The continuously variable transmission according to claim 5, characterized in that the numbers of the oil inlet holes, oil outlet holes, planetary gears, and planetary shaft gears are the same. 7. The continuously variable transmission according to claim 6, characterized in that, there are three oil inlet holes, oil outlet holes, planetary gears, and planetary shaft gears. 8. The continuously variable transmission according to claim 1, 2, 4, 5 or 7, characterized in that the hydraulic motor is a swash plate variable axial piston motor equipped with a swash plate angle control mechanism ( 6), the upper end of the swash plate (5) of the swash plate type variable axial piston motor is hingedly matched with the output end of the swash plate angle control mechanism (6). By controlling the swash plate angle, the displacement of the hydraulic motor can be controlled to carry out Continuously variable speed. 9. The continuously variable transmission according to claim 3, characterized in that, the hydraulic motor is a swash plate variable displacement axial piston motor, which is equipped with a swash plate angle control mechanism (6), and the swash plate variable displacement The upper end of the swash plate (5) of the axial piston motor is hingedly matched with the output end of the swash plate angle control mechanism (6). By controlling the swash plate angle, the displacement of the hydraulic motor can be controlled for stepless continuous speed change. 10. The continuously variable transmission according to claim 8, characterized in that, the input part further comprises a casing (14) and a distribution sleeve (17), and the casing (14) is provided with two radial holes, The flow distribution sleeve (17) is provided with a radial hole and a radial oblique hole; the swash plate type variable axial piston motor includes a flow distribution plate (7), and the flow distribution plate (7) is provided with an oil inlet groove (20) and the oil outlet groove (28), the second annular oil groove (192) sequentially passes through the radial hole on the distribution sleeve (17), one of the radial holes on the housing (14) and an oil delivery pipe (152) It communicates with the oil outlet groove (28) on the distribution plate (7), and the first annular oil groove (191) passes through the radially inclined hole on the distribution sleeve (17) and the Another radial hole and another oil delivery pipe (151) communicate with the oil inlet groove (20) on the valve plate (7). 11. The continuously variable transmission according to claim 8, characterized in that the output shaft of the swash plate type variable displacement axial piston motor is in the same body as the ring gear of the planetary gear transmission part.

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